US4020934A - Friction clutch with yieldable hydraulic operator - Google Patents

Friction clutch with yieldable hydraulic operator Download PDF

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Publication number
US4020934A
US4020934A US05/621,674 US62167475A US4020934A US 4020934 A US4020934 A US 4020934A US 62167475 A US62167475 A US 62167475A US 4020934 A US4020934 A US 4020934A
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US
United States
Prior art keywords
friction
pair
engagement
friction members
membrane
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US05/621,674
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English (en)
Inventor
Johann Eichinger
Richard Strehler
Gert Burzlauer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hurth Getriebe und Zahnraeder GmbH
Original Assignee
Carl Hurth Maschinen und Zahnradfabrik GmbH and Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19742451670 external-priority patent/DE2451670C3/de
Application filed by Carl Hurth Maschinen und Zahnradfabrik GmbH and Co filed Critical Carl Hurth Maschinen und Zahnradfabrik GmbH and Co
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Publication of US4020934A publication Critical patent/US4020934A/en
Assigned to CARL HURTH MACHINEN- UND ZAHNRADFABRIK GMBH & CO. reassignment CARL HURTH MACHINEN- UND ZAHNRADFABRIK GMBH & CO. CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). EFFECTIVE DATE 1-22-81 Assignors: CARL HURTH MASCHINEN-UND ZAHNRADFABRIK
Assigned to HURTH GETRIEBE UND ZAHNRAEDER G.M.B.H. reassignment HURTH GETRIEBE UND ZAHNRAEDER G.M.B.H. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: CARL HURTH MASCHINEN- UND ZAHNRADFABRIK GMBH
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches

Definitions

  • the invention relates to a clutch having a least one friction member which is associated with one clutch half and at least one other friction member which is associated with the other clutch half, said friction members being urgeable against each other by pressure responsive means responsive to any suitable pressure medium, and particularly to a type of such clutch including means for minimizing the shock of engagement between said plates in response to sudden application of pressure fluid.
  • Friction clutches are already known in which the friction members, for example friction plates, are urged into engagement with one another by a piston operative in a cylinder. Upon initiating an operation of such clutches, the pressure of the pressure medium often builds up suddenly, so that these clutches often move with a considerable and sudden force (German Pat. No. 862,237). It is known to diminish the impact or grab thereby occuring by providing in the hydraulic unit a pressure fluid chamber or storage cylinder. This increases the expense of the hydraulic unit and causes delay in operation (German Pat. No. 933,186).
  • a hydraulically operated clutch unit in which engagement takes place quickly through resilient load absorption.
  • a partition wall defining a counter-pressure chamber is provided within the movable coupling housing, which partition wall divides into two chambers the space defined by the housing. These two chambers are, when the clutch is uncoupled, always maintained at a relatively low pressure. Openings and valves are provided in the counter-pressure chamber, which valves are urged by the low pressure liquid into such positions as to permit the stream of liquid to flow through the openings.
  • This clutch also is very expensive (German OS No. 1,400,421 ).
  • the present invention has the major purpose of providing an easily engageable clutch having minimum grab and in which the means for minimizing such grab is provided at a minimum of manufacturing expense.
  • the basic purpose of the invention is attained by a clutch, which has resilient means comprising one wall of the chamber comprising the pressure cylinder.
  • a particularly money-saving construction is obtained by providing a yieldable membrane as the wall of the pressure cylinder opposite the clutch actuating piston.
  • a hydraulic double clutch can then be constructed by providing a pair of oppositely actuable pistons for engaging spaced sets of engageable clutch plates and positioning a yieldable wall between said pistons to divide the chamber occupied thereby into two separate clutch energizing cylinders.
  • the resilient wall may comprise a membrane fixed with respect to the clutch frame at its center and movable at its periphery with, and in sealed realtionship to, the inner surface of a surrounding chamber wall.
  • the spring characteristic of the membrane and therefore the damping characteristic of the device according to the invention can be varied by using resilient but usually metallic reinforcement on one or both sides of said resilient partition.
  • FIGS. 1 and 2 The invention is discussed in connection with exemplary embodiments which are illustrated in FIGS. 1 and 2.
  • FIG. 1 illustrates schematically an exemplary embodiment of the invention.
  • FIG. 2 illustrates a different exemplary embodiment of the invention.
  • FIG. 1 illustrates schematically a longitudinal cross-sectional view of a hydraulically shiftable double clutch.
  • a shaft 1 is to be selectively coupled with gears 2, 3 which are supported rotatably on the shaft by bearings 4.
  • Two clutch housings 5, 6 are arranged centrally with respect to and adjacent said gears and are connected fixedly with respect to rotation by teeth to said gears.
  • So-called outer plates 7, 8 conventionally engage said clutch housings. For this purpose they have external teeth, which project into corresponding slots of the clutch housings.
  • So-called inner plates 9, 10 are arranged between the outer plates, which inner plates are provided conventionally with internal teeth which engage external teeth connected fixedly with respect to rotation to the shaft.
  • the said external teeth are provided on each clutch sleeve 11, 12, of each of which is arranged fixedly with respect to rotation on the shaft, for which purpose corresponding splines 13 are provided.
  • the external teeth can also be arranged directly on the shaft.
  • a pressure plate 14, 15 is provided between each respective clutch sleeves and the gears.
  • Two supply control sleeves 16, 16' are supported between the two clutch sleeves on the shaft and bear against one another in the center of the clutch.
  • the two supply control sleeves can also be united to a single one.
  • the pressure plates, clutch sleeves and supply control sleeves are held together by screws 17, whereby the pressure plates rest against shoulders of the shaft and are thus held axially.
  • Two pistons 18, 19 are supported longitudinally movably on the supply control sleeves 16, 16'.
  • the bearing points have seals 20.
  • Springs 21, 21' lie between the pistons 19, 18 respectively and the respective clutch sleeves 11, 12 and urge both axially apart.
  • the springs are initially tensioned because they bear in the rest control position against the shoulder 22 of the supply control sleeve.
  • the pistons 18, 19 are surrounded by a cylindrical sleeve 23.
  • the pistons are secured against axial shifting relatively to the sleeve toward the openings of the sleeve by snap rings 23' or the like. If thus the piston 18 is for example moved to the left, the piston 19 is carried along through the snap rings and the sleeve 23.
  • the pressure of the springs 21' acts only onto the so-energized piston and not onto the other one.
  • a partition wall exists in the center between the two pistons, which is constructed according to the invention as a resilient membrane 24.
  • Said membrane is sealingly centered and axially held at its inner circumference on the supply control sleeves, for which purpose the supply control sleeves have corresponding shouldered portions.
  • the axial mounting can also be accomplished in other ways as desired, for example by snap rings.
  • the membranes engages at its outer periphery an annular groove 25, which is provided in a piston ring 26.
  • the annular groove is advantageously constructed such that the side walls thereof converge outwardly.
  • the membrane is in this area tapered correspondingly such that it lies snugly in the piston ring, provided however, that a small movement between the piston ring and membrane is permitted in order that the membrane can bend.
  • the piston ring bears against the inner wall of the sleeve.
  • the discontinuity (not shown) of the piston ring is sealed conventionally, as by overlapping same. It would also be possible to use a so-called O-ring as seal if the membrane is constructed such that the O-ring can be received by it.
  • the membrane can also be sealed in other ways, for example by prevulcanized packing washers which can be very advantageous.
  • the space which is enclosed by the sleeve and the piston is divided by the membrane into two chambers 27, 28, which can selectively be pressurized with pressure medium, for example oil, in any conventional manner.
  • pressure medium for example oil
  • two conduits are provided in the shaft, of which the one is shown and identified with reference numeral 29. From these conduits communication is provided through respectively connected radial openings 30, thence respectively through a pair of annular grooves 31 and connected openings 32 to the said chambers. Pressure medium is thus introduced into, or discharged from said chambers by means of the conduits 29 and their respective connecting paths.
  • radial connecting openings 34 are provided in the shaft, which openings 34 lead the lubricant into the clutch, from where it can reach the plates through annular recesses 35, the passage holes for the screws 17 and slots 36, which are provided in the clutch sleeves.
  • the chamber 28 is connected to the return passageway.
  • the control means herefore are known and are therefore not shown.
  • the piston 18 moves to the left and takes along the piston 19 through the sleeve 23.
  • the membrane yields to the right due to the pressure increase and thus absorbs the impact.
  • supporting cup springs 37, 38 or the like are provided on both sides of the membrane 24, which cup springs change the spring characteristic of the membrane.
  • the illustration in FIG. 2 is only exemplary for the thickness of the membrane and form and number of the supporting springs can be varied freely depending on the desired spring characteristic and damping action of the membrane.
  • the invention has the advantage that the damping device can be installed virtually without additional effort over conventional designs, and hence without additional cost, because the partition wall must in any case be present in double clutches.
  • the only change involved is that the membrane is usually constructed thinner than the conventional partition wall and it is made of a resilient material.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
US05/621,674 1974-10-31 1975-10-14 Friction clutch with yieldable hydraulic operator Expired - Lifetime US4020934A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19742451670 DE2451670C3 (de) 1974-10-31 Hydraulisch schaltbare Doppel-Reibungskupplung
DT2451670 1974-10-31

Publications (1)

Publication Number Publication Date
US4020934A true US4020934A (en) 1977-05-03

Family

ID=5929644

Family Applications (1)

Application Number Title Priority Date Filing Date
US05/621,674 Expired - Lifetime US4020934A (en) 1974-10-31 1975-10-14 Friction clutch with yieldable hydraulic operator

Country Status (8)

Country Link
US (1) US4020934A (OSRAM)
JP (1) JPS5221547A (OSRAM)
AU (1) AU8574475A (OSRAM)
BR (1) BR7507068A (OSRAM)
FR (1) FR2289797A1 (OSRAM)
GB (1) GB1471516A (OSRAM)
IT (1) IT1047568B (OSRAM)
ZA (1) ZA756313B (OSRAM)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4153148A (en) * 1977-06-02 1979-05-08 D. A. B. Industries, Inc. Clutch with replacable disc and motor assemblies
US4289221A (en) * 1978-11-17 1981-09-15 Eaton Corporation Hydraulic control system
CN104235224A (zh) * 2014-09-13 2014-12-24 吉林大学 一种湿式双离合器
US20200217381A1 (en) * 2017-09-22 2020-07-09 Brl Brake Solutions, S.L. Brake Device

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6293342U (OSRAM) * 1985-12-03 1987-06-15
JP2004107020A (ja) * 2002-09-18 2004-04-08 Oki Electric Ind Co Ltd 紙葉類搬送装置および紙葉類搬送用ベルト
CN108166688B (zh) 2017-05-08 2019-11-05 宁波万汇休闲用品有限公司 遮蔽篷装置

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2620814A (en) * 1947-03-04 1952-12-09 Hobbs Transmission Ltd Centrifugally actuated fluid control valve
US2621769A (en) * 1947-05-15 1952-12-16 Cardwell Mfg Company Inc Flexible plate clutch or brake
US2809308A (en) * 1952-12-12 1957-10-08 Singer Mfg Co Actuating mechanisms for electric clutch-brake motors
US3098549A (en) * 1961-09-26 1963-07-23 Allis Chalmers Mfg Co Double acting hydraulic actuator
US3335836A (en) * 1966-03-07 1967-08-15 Caterpillar Tractor Co Accumulator for clutch actuating pistons
US3612237A (en) * 1968-05-16 1971-10-12 Honda Motor Co Ltd Liquid pressure-operated frictional clutch apparatus

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE646992A (OSRAM) * 1963-04-26

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2620814A (en) * 1947-03-04 1952-12-09 Hobbs Transmission Ltd Centrifugally actuated fluid control valve
US2621769A (en) * 1947-05-15 1952-12-16 Cardwell Mfg Company Inc Flexible plate clutch or brake
US2809308A (en) * 1952-12-12 1957-10-08 Singer Mfg Co Actuating mechanisms for electric clutch-brake motors
US3098549A (en) * 1961-09-26 1963-07-23 Allis Chalmers Mfg Co Double acting hydraulic actuator
US3335836A (en) * 1966-03-07 1967-08-15 Caterpillar Tractor Co Accumulator for clutch actuating pistons
US3612237A (en) * 1968-05-16 1971-10-12 Honda Motor Co Ltd Liquid pressure-operated frictional clutch apparatus

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4153148A (en) * 1977-06-02 1979-05-08 D. A. B. Industries, Inc. Clutch with replacable disc and motor assemblies
US4289221A (en) * 1978-11-17 1981-09-15 Eaton Corporation Hydraulic control system
CN104235224A (zh) * 2014-09-13 2014-12-24 吉林大学 一种湿式双离合器
US20200217381A1 (en) * 2017-09-22 2020-07-09 Brl Brake Solutions, S.L. Brake Device
US11635119B2 (en) * 2017-09-22 2023-04-25 Brl Brake Solutions, S.L. Brake device

Also Published As

Publication number Publication date
AU8574475A (en) 1977-04-21
IT1047568B (it) 1980-10-20
ZA756313B (en) 1976-09-29
BR7507068A (pt) 1976-08-03
GB1471516A (en) 1977-04-27
JPS55613B2 (OSRAM) 1980-01-09
JPS5221547A (en) 1977-02-18
FR2289797A1 (fr) 1976-05-28
DE2451670A1 (de) 1976-05-13
DE2451670B2 (de) 1977-02-10
FR2289797B3 (OSRAM) 1979-06-29

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Legal Events

Date Code Title Description
AS Assignment

Owner name: CARL HURTH MACHINEN- UND ZAHNRADFABRIK GMBH & CO.

Free format text: CHANGE OF NAME;ASSIGNOR:CARL HURTH MASCHINEN-UND ZAHNRADFABRIK;REEL/FRAME:003935/0487

Effective date: 19810122

AS Assignment

Owner name: HURTH GETRIEBE UND ZAHNRAEDER G.M.B.H.

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:CARL HURTH MASCHINEN- UND ZAHNRADFABRIK GMBH;REEL/FRAME:005887/0043

Effective date: 19911011